Spinning and twisting spindle

ABSTRACT

The spindle is rotatably mounted within a sleeve by means of a neck bearing and a foot bearing while the sleeve is mounted elastically within a fixed bolster. An elastic radially symmetrical connecting element serves to mount the upper end of the sleeve in the bolster while an elastic radially symmetrical connecting member connects the lower end of the sleeve to the bolster. The lower connecting member may also support the sleeve rigidly in an axial direction relative to the bolster in some embodiments.

[ Mar. 26, 1974 United States Patent 1191 Mandl SPINNING AND TWISTINGSPINDLE FOREIGN PATENTS OR APPLICATIONS ,m .m aa Huh" ff n BB mm eei nmrrar GGhF 45706 60465 99999 lllli 309 2 ll 75627 77750 .9 .9 21592 5 2459 42 5 1 u m h L t r E SE .m mm W o e W2 I ah m mw n i a h Md cf. m n mn an re h mm rzl e.- ew .1 GS RW n a w m m n v w m A .i 11 5 3 7 7 r1 r1[22] Filed: Feb. 1, 1972 [21] Appl. No.: 222,593

Primary Examiner-John Petrakes Assistant Examiner-Charles GorensteinAttorney, Agent, or Firm-Kenyon & Kenyon Reilly Carr & ChapinSwitzerland.................v....... 1582/71 ABSTRACT The spindle isrotatably mounted within a sleeve by 3 i2 V H 4 6 B5 5 Am BO 5 Lil 3 r 1w NO 3 M .m F QM 5 to mount the upper end of the sleeve in the bolsterwhile an elastic radially symmetrical connecting memb [56] ReferencesCited UNITED STATES PATENTS er connects the lower end of the sleeve tothe bol- Taft Westall et al. Hargreaves et Schmid MY uu I m w Wmv l l llJflnv l hhi'fl-ill'ill 9' 1 2 I SPINNING AND TWISTING SPINDLE Thisinvention relates to a spinning and'twisting spindle. More particularly,this invention relates to a spindle for use in a spinning or twistingmachine for staple fiber spinning as well as for use in drawtwistingmachines for processing endless filaments.

Heretofore, spinning and twisting spindles for various types of spinningor twisting machines and drawtwisting machines have been known in whicha spindle shaft is mounted by means ofa neck bearing and a foot bearingwithin a bolster. However, as the neck bearing has usually been rigidlyconnected to the bolster, vibrations have been transmitted to thespindle rail and to the whole machine, especially at high spindlespeeds. As a consequence, a high noise level of the bearing as well as ahigh loading of the neck bearing and the spindle shaft have been caused.

ln order to overcome these problems, the bolster has been mounted in aflexible or resilient manner to the spindle rail by means of a pressuremember surrounding the bolster helically or as a pot. Such a pressuremember has usually been supported by the spindle rail directly or via anelastic support member on the underside of the spindle rail. Inaddition, other elastic support members of similar construction havebeen positioned between the upper side of the spindle rail and thebolster flange. Arrangements of this type, however, cannot ensuresufficient dampening at high spindle speeds and their life isunsatisfactorily short. Also, elastically mounting the neck bearing inthe bolster by means of a rubber or Vulcollan ring or similar deviceshas not proved satisfactory as these devices inherently cannot yieldenough. Such rings are also subject to considerable wear, as they aresubject to alternating loads and because the torque to be taken upfrequently causes rotation of the rubber rings.

Further, it has been known to mount the neck bearing within a sleeve andto position a sandwich tube between the sleeve and the bolsterabove adampening spiral member which is placed between the sleeve and bolster.These sandwich tubes usually consist of two concentric metal sleeveswith an elastomer layer inbetween. ln this manner, resilient lateralyielding of the neck bearing is made possible. However, the concentricmetal sleeves must be manufactured with very high precision in order toensure precise positioning with the adjacent parts, i.e., with thebolster on one hand and with the inner sleeve on the other hand.Further, as the elastomer layer should not be subject ,to axial load,the metal sleeves must be pressed simultaneously into the bolster andonto the inner sleeve, achievement of which, is very difficult. Stillfurther, resilient materials such as rubber, Vulcolland, etc., to beused in the elastic sandwich layer cannot withstand alternating loadsand are subject to excessive wear, and the useful life span of suchlayers is severely shortened under the influence of oil and fiberpreparation fluids. As a consequence, frequent replacement has beennecessary. This, of course, implys a complicated disassembling andassembling of the bolsters.

A further disadvantage of the elastic sandwich layer of a sandwich tube,assuming the overall dimensions are maintained, is that if a specificradial flexibility is chosen, the cardanic flexibility is alsodetermined automatically. Thus, the flexibilities cannot be chosenindependently and thus cannot, or only unsatisfactorily, be

optimized. As a result, undesirably high bearing loads occur.Furthermore, the use of the elastomer sandwich layer results intemperature differences of the elastic material of the sandwich layerfrom spindle to spindle, due to unavoidable differences of imbalancecaused, e.g. by different tube excentricities and varying unbalance ofthe yarn packages being built. Thus, the critical rotational speedsdiffer from spindle to spindle and vary over the build up of the yarnpackage. The resulting enlargement of the overall range of possiblecritical spindle speeds of the totality of spindles of a machinecorrespondingly reduces the range of noncritical spindle speedsavailable for operation. The range of application of the machine, thus,is impaired undesirably due to the behavior of the rubber sandwichlayer.

It is also noted that differing dampening properties result from thetemperature differences mentioned of the elastomer layers. This is adisadvantage which results in differing operating characteristics of thespindles. As resonances also occur on spindles rotating at noncriticalspeeds, which resonances are caused by the impulses of the drive tapejoint and by the variations of yarn tension, i.e., to the rotation ofthe spindle itself, vibrations are superimposed. This adds further yarntensions to the yarn tension already present and thus increases thedanger of end breakages.

Also, the resulting force transmitted from the spindle drive tape to thespindle whorl is not compensated for by the sandwich tube. Thus, theinner sleeve is inclined with respect to the bolster and the dampingelement arranged between the bolster and the inner sleeve, e.g. thedampening spiral, is unilaterally deformed. As a result, the dampeningeffect of the dampening element becomes direction-dependent and thegeometrical axis of rotation of the spindle is forced into a path in aroughly elliptical cone surface with the obvious disadvantages resultingfrom this.

Accordingly, it is an object of the invention to reduce the bearingloads for a spindle used in a spinning or twisting machine to a minimum.

It is another object of the invention to achieve conditions under whichthe axis, about which the rotating parts of a spindle including a yarnpackage actually rotates, can approach the axis of inertia through thecenter of gravity as closely as possible.

It is another object of the invention to elastically mount a spindlewithin a bolster in a manner to avoid wear on the elastic mountingmembers.

It is another object of the invention to have a spindle mountingwithstand large eccentricities.

It is another object of the invention to reduce noise levels and totransmit minimal vibrations to the machine in which a spindle ismounted.

It is another object of the invention to extend the useful life ofspindles and their mountings.

It is another object of the invention to provide a universal range ofapplicability of a spindle with respect to yarn package weight as wellas to operational spindle speeds.

Briefly, the invention provides an arrangement for mounting a spindle ina bolster which can be rigidly secured to a spindle rail. Thearrangement includes the combination of a rigid sleeve in which a neckbearing and a foot bearing are mounted to receive and rotatably supporta spindle shaft, a radially symmetrical dampening element between thesleeves and bolster, and a pair of radially symmetrical elastic memberswhich connect opposite ends of the sleeve to the bolster. In addition,the sleeve is supported on the bolster at the lower end in a rigidmanner axially thereof.

In one embodiment, in order to provide for a rigid axial connectionbetween the sleeve and bolster, the sleeve is slidably mounted in thebottom of the bolster. In another embodiment, the lower elastic memberis connected between the bottom of the sleeve and the bolster so as torigidly support the sleeve in a vertical plane. In such an embodiment, aspring rod or a helically coiled wire spring is used for the elasticmember. Further, in this latter embodiment the upper elastic member isformed as an apertured disc having a spiral slot therein which serves toimpart elastic characteristics to the member.

These and other objects and advantages of the invention will become moreapparent from the following detailed description and appended claimstaken in conjunction with the accompanying drawings in which:

FIG. 1 illustrates a schematic view of a spindle bearing arrangementaccording to the invention;

FIG. 2 illustrates a schematic view of a modified spindle bearingarrangement according to the invention;

FIG. 3 illustrates a detailed longitudinal section of a further spindlebearing arrangement according to th invention;

FIG. 4 illustrates a cross-sectional view of the upper connecting memberof FIG. 3; and

FIG. 5 illustrates an axonometric view of the lower connecting member ofFIG. 3.

Referring to FIG. 1, a spindle shaft 1 on which a yarn package 2 iswound is rotatably supported by two bearings 3 and 4 axially andradially in a rigid inner sleeve 5. The inner sleeve 5 is connected in aradially symmetrically manner via two elastic spring members 6 and 7 ofgreat softness, e.g.springs, in two different planes with a bolster orcasing 8 so as to be radially movable. The bolster 8 is, in turn,rigidly fixed to a spindle rail 9. The inner sleeve 5 is also supportedon the bottom part 10 of the bolster 8 so as to be rigidly disposedrelative to the bolster 8 in the axial direction while being movableradially. Furthermore, dampening elements 11 and 12 which are eachradially symmetrical are provided between the sleeve 5 and theside-walls of the bolster 8.

In operation, the spindle dynamically behaves as follows.

Of the axes shown in FIG. 1, one represents the free axis A, about whichthe spindle would rotate in the absence of bearing forces actingthereon. This axis A is identical with one of the main axes of inertiathrough the center of gravity S. The outer forces necessarily acting onthe spindle, such as bearing guiding forces, yarn tension, etc.,influence the spindle in such manner that all rotating elements of thespindle including the yarn package 2 rotate not about this free axis Abut about another axis, namely an axis of actual rotation B at anangular velocity W. The free axis A of the rotating spindle includingthe yarn package generally also does not coincide with the axis Cdetermined by the geometry of the guiding elements (i.e., the bearings 3and 4). This is prevented by imprecisions of the package tube seat,deformed package tubes and irregular yarn package formation, etc. Inorder to keep the bearing loads to a minimum under these conditions,i.e. in order to permit rotation of the yarn package 2 and all otherelements of the spindle rotating about the axis of actual rotation B asclosely as possible to the free axis -A, the spring constants of theelastic members 6 and 7 are kept as low as possible. That is, theelastic members 6 and 7 are chosen very soft. As, however, at increasingrotational speeds, the mass forces generated by the movable butnon-rotating elements (dead masses") increase, their influence on thebearing loads at increasing rotational speeds relatively soon outweighsthe spring forces, which are low in any event. Thus, the maximumrotational speed permissible is limited by the magnitude of these massforces. In order to elevate this limit as high as possible, the innersleeve 5 must be very light, i.e., with a minimum wall thickness justensuring the rigidity between the two bearings 3 and 4. If a light metalsleeve is chosen, the mass forces can be reduced further.

Referring to FIG. 2, wherein like parts as above are similarlyillustrated, the spindle bearing arrangement which is based on the sameprinciple as the arrangement shown in FIG. 1, has an inner sleeve 13supported by a friction-free and, thus, wear-free spring rod 14 insteadof being supported by a friction-generating surface. The spring rod 14is soft in the radial direction but very stiff in the axial direction.The dynamic behavior of the arrangement in principle is the same as thatdescribed with reference to FIG. I, thus a further description is notbelieved to be necessary.

Referring to FIG. 3, the bearing arrangement is preferably constructedto cooperate with a bolster or bearing housing 15 which is fixed inknown manner via a flange 17 on a spindle rail 16. The bolster 15 isprovided with a cylindrical lower part 18 which extends verticallydownard, as viewed, and with a bottom 19 containing an opening 20.Between the bolster flange I7 and a cover flange 21, an upper radiallysymmetrical elastic spring connecting member 22 is fixed along thecircumference by means of detachable screws 23. The elastic member 22has a central bore 24 into which a thin-walled, and thus light, butrigid inner sleeve 25 is pressed in. The sleeve 25 in turn mounts a neckbearing 26 in the upper part which neck bearing 26 is constructed as ananti-friction bearing for rotatably receiving a spindle shaft 27. Thelower end of the sleeve 25 has a foot bearing 28 rigidly mountedtherein. In addition, a lower elastic connecting member 29 which also isradially symmetrical has an upper vertical end fixed rigidly in the footbearing 28. The other vertical end of the lower connecting member 29 isrigidly mounted in a support member 30, which is provided with a stud 31protruding through the larger opening 20, so that the stud 31 can beadjusted and fixed by means of a nut 32 in a certain chosen position. Agasket 33 seals the opening 20 against oil leakage. A dampening spiral33' is also arranged between the bolster l8 and the inner sleeve 25 in amanner as is known.

The elements which serve to substantially determine the dynamic behavoirof the spindle bearing arrangement are constructed as follows.

The upper elastic spring connecting member 22 is constructed as a metaldisc of uniform thickness, the radial elasticity of which is obtained bystamping out one spiral slot 34 (FIG. 4) beginning near the inner. bore24 and ending near the outer circumference. The elastic properties ofthe metal disc are thus practically radially symmetrical. Of course, aplurality of spiral slots also can be chosen, if desired. The thicknessof the connecting member 22 is determined according to the materialchosen (e.g. spiral steel) and, if a certain spring constant for theradial direction is chosen, according to the requirements of rationalmanufacturing methods (e.g. stamping), to the outside diameter, as wellas to the shape of the spiral slot 34 itself. The dimensions of theslotted metal disc also determine the spring constant in the axialdirection, which as a rule is considerably smaller than the one in theradial direction, but which in this member is of no consequence. Thus,e.g. for a drawtwisting spindle rotating at a fast speed at about 10,000r.p.m., with yarn package weights commonly used today of 2-4 kilograms(kg), using corresponding spindle dimensions, the spring constant in theradial direction K is chosen below 30 kilograms per millimeter (kg/mm).

The lower elastic spring connecting member 29 is also of simpleconstruction taking the shape of a helical steel spring. This member- 29is practically radially symmetrical, i.e., the spring constant in theradial direction does not depend on the direction. The spring constantin the radial direction K can be chosen somewhat lower than that of theupper connecting member 22.

The spring constant in the axial direction, however, must be very high,i.e., the spring rod 29 should be practically rigid in the axialdirection in order to carry the weight of the spindle and of the yarnpackage. For example, for the aforementioned drawtwisting. spindle, thespring constant in the radial direction K should be below kilograms permillimeter (kg/mm) and in the axial direction K above 50 kg/mm, Suchsteel springs are advantageous insofar as they are resistant toalternating loads if their dimensions are chosen correctly, in whichrespect they differ favorably from elastomers.

The light, thin-walled, inner sleeve 25 can be made from steel orpreferably from light metal. If the weight does not exceed one-tenth toone-fifth of the full yarn package weight, the sleeve weight should meetthe requirements with respect to the magnitude of this mass.

The advantages obtained from the spindle bearing arrangement describedabove are simplicity of construction and, thus, economical manufacturingof the few parts needed, and simplicity of assembly work. Further, theconnection of the inner sleeve in a manner which is free of friction andwear and which is elastic in the radial direction serves to increase thelife span of all members subject to alternating loads. Further, as nodisplacement of the spindle shaft relative to the bearings can occur dueto the radially elastic support of the rigid inner sleeve, small bearingclearances and, thus, low noise levels and long life of the neck andfoot bearings can be realized.

A further advantage is the adjustability of the position of the supportmember and, thus, of the lower connecting member which permits fullcompensation of an inclination of the inner sleeve caused by the drivingtape tension. In addition, large eccentricities can be tolerated alongwith higher rotational speeds and higher yarn package weights. Also,another advantage resides in that larger deviations of the package tubeseats from concentricity can be tolerated.

Use of the inventive spindle bearing arrangement also allows the bolsterto be fixed rigidly to the spindle rail. The advantages resulting fromthis are that the spindle can be plumbed easily and that anydisplacement with respect to the spindle rail in the radial as well asin the axial'direction is excluded. The bolster, thus,

cannot be inclined under the influence of impacts from the outside.Further, since the bolster is rigidly fixed to the spindle rail, itsposition cannot-be altered by contaminations during operation. This,according to experience, is a considerable advantage. v

The inventive arrangement furthermore presents the advantage that noreplacement parts are needed, the

support seats of which could cause fitting rust formation. As a furtheradvantage, owing to the fixed mounting of the bolster on the spindlerail, assembly of a fixed arrangement of a spindle brake can be effectedeasily.

Another advantage is that the soft connection via the elastic membersresults in a low critical speed of rotation. This is important, as, inthis case, smaller bearing loads are generated and, as the practicablerange of spindle speeds is larger with respect to the critical speed, sothat at low yarn package weights at which inherently the critical speedis higher, the critical speed can still be maintained at a low level.Reduction of the bearing loads to a minimum also proves advantageous inthat a lighter inner sleeve can be used to ensure the rigidity neededfor keeping the bearings mutually coaxial and the small mass of theinner sleeve cannot reduce the upper admissible limit of the spindlespeed noticeably.

What is claimed is:

1. In combination a spindle rail;

at least one bolster rigidly fixed on said spindle rail;

a spindle shaft;

a rigid sleeve disposed about said shaft and rigidly supported on saidbolster in an axial direction of said sleeve;

a neck bearing rotatably mounting said shaft in said sleeve;

a foot bearing rotatably mounting a lower portion of said shaft in saidsleeve;

a radially symmetrical dampening element disposed between said sleeveand said bolster;

a first radially symmetrical elastic spring member connecting saidsleeve to said bolster to one side of said dampening element, said firstelastic spring member being an apertured disc having a continuous outercircumferential surface, a continuous inner circumferential surface anda spiral slot between said surfaces; and

a second radially symmetrical elastic spring member connecting saidsleeve to said bolster on an opposite side of said dampening element.

2. The combination as set forth in claim 1 wherein said first elasticspring member has a spring constant in a radial direction lower than 30kilogram per millimeter. I

3. The combination as set forth in claim 1 wherein said second elasticspring member has a spring constant- 6. The combination as set forth inclaim wherein said spindle shaft is disposed in a vertical plane withsaid spring rod disposed therebelow.

7. The combination as set forth in claim 1 wherein said second elasticmember is a helically coiled spring wire having one end fixed to saidfoot bearing and an opposite end fixed to said bolster; said spring wiregenerating radially uniform spring forces.

8. The combination as set forth in claim 1 wherein said second elasticmember is adjustable laterally of said bolster.

9. The combination as set forth in claim 1 wherein said first and secondspring members are made of metal.

10. In combination a bolster;

a spindle shaft;

a rigid sleeve disposed about said shaft and rigidly supported on saidbolster in an axial direction of said sleeve;

a radially symmetrical dampening element disposed between said sleeveand said bolster;

a first radially symmetrical elastic spring member connecting saidsleeve to said bolster above said dampening element, said first elasticspring memher being an apertured disc having a continuous outercircumferential surface, a continuous inner circumferential surface anda spiral slot between said surfaces; and

a second radially symmetrical elastic spring member connecting saidsleeve to said bolster below said dampening element.

11. The combination as set forth in claim 10 wherein said second elasticspring member supports said sleeve on said bolster in a rigid manneraxially of said shaft.

12. The combination as set forth in claim 10 wherein said first elasticspring member has a spring constant in a radial direction lower than 30kilograms per millimeter and said second elastic spring member has aspring constant in a radial direction lower than l5 kilograms permillimeter.

13. In combination a bolster;

a rigid sleeve concentrically disposed within said bolster',

a radial symmetricalv dampening'element disposed between said sleeve andsaid bolster;

a first radially symmetrical elastic spring member connecting saidsleeve to said bolster above said dampening element, said first elasticspring member being an apertured disc having a continuous outercircumferential surface, a continuous inner circumferential surface anda spiral slot between said surfaces; and

a second radially symmetrical elastic spring member connecting saidsleeve to said bolster below said dampening element 14. The combinationas set forth in claim 13 wherein said second elastic spring member is aradially movable spring rod having one end fixed to said sleeve and anopposite end fixed to said bolster, said spring rod being rigid axiallyof said sleeve to rigidly support said sleeve on said bolster in saidaxial direction of said sleeve.

15. The combination as set forth in claim 13 wherein said second elasticmember is a helically coiled spring wire having one end fixed to saidsleeve and an opposite end fixed to said bolster, said spring wiregenerating radially uniform spring forces.

16. The combination as set forth in claim 13 which further includes afoot bearing within said sleeve at a lower end and a neck bearing withinsaid sleeve at an upper end to receive and rotatably support a shaftspindle therein.

1. In combination a spindle rail; at least one bolster rigidly fixed onsaid spindle rail; a spindle shaft; a rigid sleeve disposed about saidshaft and rigidly supported on said bolster in an axial direction ofsaid sleeve; a neck bearing rotatably mounting said shaft in saidsleeve; a foot bearing rotatably mounting a lower portion of said shaftin said sleeve; a radially symmetrical dampening element disposedbetween said sleeve and said bolster; a first radially symmetricalelastic spring member connecting said sleeve to said bolster to one sideof said dampening element, said first elastic spring member being anapertured disc having a continuous outer circumferential surface, acontinuous inner circumferential surface and a spiral slot between saidsurfaces; and a second radially symmetrical elastic spring memberconnecting said sleeve to said bolster on an opposite side of saiddampening element.
 2. The combination as set forth in claim 1 whereinsaid first elastic spring member has a spring constant in a radialdirection lower than 30 kilogram per millimeter.
 3. The combination asset forth in claim 1 wherein said second elastic spring member has aspring constant in a radial direction lower than 15 kilograms permillimeter.
 4. The combination as set forth in claim 1 wherein saiddampening element is a dampening spiral member.
 5. The combination asset forth in claim 1 wherein said second elastic spring member is aradially movable spring rod having one end fixed to said foot bearingand an opposite end fixed to said bolster, said spring rod being rigidaxially of said shaft to rigidly support said sleeve on said bolster insaid axial direction of said sleeve.
 6. The combination as set forth inclaim 5 wherein said spindle shaft is disposed in a vertical plane withsaid spring rod disposed therebelow.
 7. The combination as set forth inclaim 1 wherein said second elastic member is a helically coiled springwire having one end fixed to said foot bearing and an opposite end fixedto said bolster, said spring wire generating radially uniform springforces.
 8. The combination as set forth in claim 1 wherein said secondelastic member is adjustable laterally of said bolster.
 9. Thecombination as set forth in claim 1 wherein said first and second springmembers are made of metal.
 10. In combination a bolster; a spindleshaft; a rigid sleeve disposed about said shaft and rigidly supported onsaid bolster in an axial direction of said sleeve; a radiallysymmetrical dampening element disposed between said sleeve and saidbolster; a first radially symmetrical elastic spring member connectingsaid sleeve to said bolster above said dampening element, said firstelastic spring member being an apertured disc having a continuous outercircumferential surface, a continuous inner circumferential surface anda spiral slot between said surfaces; and a second radially symmetricalelastic spring member connecting said sleeve to said bolster below saiddampening element.
 11. The combination as set forth in claim 10 whereinsaid second elastic spring member supports said sleeve on said bolsterin a rigid manner axially of said shaft.
 12. The combination as setforth in claim 10 wherein said first elastic spring member has a springconstant in a radial direction lower than 30 kilograms per millimeterand said second elastic spring member has a spring constant in a radialdirection lower than 15 kilograms per millimeter.
 13. In combination abolster; a rigid sleeve concentrically disposed within said bolster; aradial symmetrical dampening element disposed between sAid sleeve andsaid bolster; a first radially symmetrical elastic spring memberconnecting said sleeve to said bolster above said dampening element,said first elastic spring member being an apertured disc having acontinuous outer circumferential surface, a continuous innercircumferential surface and a spiral slot between said surfaces; and asecond radially symmetrical elastic spring member connecting said sleeveto said bolster below said dampening element.
 14. The combination as setforth in claim 13 wherein said second elastic spring member is aradially movable spring rod having one end fixed to said sleeve and anopposite end fixed to said bolster, said spring rod being rigid axiallyof said sleeve to rigidly support said sleeve on said bolster in saidaxial direction of said sleeve.
 15. The combination as set forth inclaim 13 wherein said second elastic member is a helically coiled springwire having one end fixed to said sleeve and an opposite end fixed tosaid bolster, said spring wire generating radially uniform springforces.
 16. The combination as set forth in claim 13 which furtherincludes a foot bearing within said sleeve at a lower end and a neckbearing within said sleeve at an upper end to receive and rotatablysupport a shaft spindle therein.